Threaded pipe connection having a retainer gasket with pressure relief vents

ABSTRACT

A connection for threaded pipes and other tubular sections including a gasket for interposition between a first and an opposing second interface surface of the connection. The gasket includes a retainer and a generally annular seal element received in a groove formed into at least one side of the retainer. Such retainer side further is formed as having one or more channels extending extend radially through the groove and the inner or outer perimeter of the retainer. Each such channel defines a vent for relieving hydrostatic fluid pressure as the gasket is compressed between the interface surfaces.

CROSS REFERENCE TO RELATED APPLICATIONS

[0001] This application is a continuation of U.S. application Ser. No.09/922,410, filed Aug. 3, 2001, entitled “Threaded Pipe Connection withImproved Seal,” the disclosure of each of which is expresslyincorporated herein by reference, and of U.S. application Ser. No.10/091,230, filed Mar. 5, 2002, entitled “Retainer Gasket with PressureRelief Vents,” which application claims the benefit of the filing dateof U.S. Provisional Application Serial No. 60/279,503, filed Mar. 28,2001, the disclosure of each of which is expressly incorporated hereinby reference.

BACKGROUND OF THE INVENTION

[0002] The present invention relates broadly to an assembly for joiningthreaded pipes and other tubular sections, and more particularly to suchan assembly which is adapted for use with a pressure-venting gasket.

[0003] In basic construction, gaskets of the type herein involved areformed of a relatively compressible, annular seal member having acentral aperture configured for registration with the correspondingmargins of a pair of mating surfaces. The seal member is supported by anannular metal or plastic retainer which may be machined, stamped, moldedor otherwise formed to conform to the surface geometry of the matingsurfaces. Particularly, the seal member may be molded-in-place ormounted in a groove formed into one or both sides of the retainer, orabout the inner and/or outer periphery of the retainer to form anintegral gasket structure. Representative such gaskets are shown, forexample, in U.S. Pat. Nos. 3,195,906; 3,215,442; 3,259,404; 3,578,346;3,635,480; 3,720,420; 3,746,348; 4,026,565, 4,625,978, and are marketedcommercially by the O-Seal Division of Parker-Hannifin Corporation, SanDiego, Calif., under the tradenames “Gask-O-Seal” and “Integral Seal.”

[0004] Retainer gaskets of the type herein involved are employed in avariety of sealing applications, such as in commercial, industrial, ormilitary equipment, vehicles, or aircraft for compression between theopposing or faying surfaces of a pair of mating parts or structures toprovide a fluid-tight interface sealing thereof. In service, the gasketis clamped between the mating surfaces to effect the compression anddeformation of the seal member and to develop a fluid-tight interfacewith each of those surfaces. The compressive force may be developedusing a circumferentially spaced-apart arrangement of bolts or otherfastening members, or by a threaded engagement of the mating parts.

[0005] Particularly for oil and gas well drilling assemblies such asdescribed in U.S. Pat. Nos. 4,846,507 and 5,015,017, as well as forother applications involving the sealing of casings, tubing, pipes,lines, or other tubular members connected by means of a threaded pipejoint or other coupling, there exists a need to relieve internalhydrostatic fluid pressure which may be developed as a result ofthreading compound or other fluid being trapped between the threads ofthe coupling and the tubular members being joined. In this regard,damage to the gasket and/or the to the joint may result if the pressurewhich is developed is not relieved from the joint as the parts are beingthreadably engaged.

[0006] In view of the foregoing, it is believed that improvements inretainer gaskets for oil and gas well drilling and other applicationswould be well-received by the industries concerned. A preferred gasketconstruction would be economical to manufacture, but also would exhibitreliable sealing performance. Such a gasket additionally would allow forthe venting of internally-developed fluid pressure.

BROAD STATEMENT OF THE INVENTION

[0007] The present invention is directed to a retainer gasketconstruction particularly adapted for venting hydrostatic pressurebetween a pair of mating interface surfaces which pressure is developedfrom a source of fluid trapped as one or both of the surfaces aredisplaced to compress the gasket in forming a fluid-tight sealtherebetween. The mating interfacing surfaces may be, particularly, anend face of an internally or externally-threaded pipe, shaft, or tubing,or other tubular member, and a shoulder, ledge, land, or otherconfronting surface of a matingly-threaded coupling which may be usedfor joining the tubular member to another such member. The gasket of theinvention may be interposed and compressed between the interfacesurfaces to provide a fluid-tight seal therebetween.

[0008] The fluid source may be joint compound which is commonly appliedas a lubricant and/or sealant to the threads of the member and/orcoupling. As the member and coupling are screwed together, the compoundis extruded from the enmeshing threads and may become trapped betweenthe mating interface surfaces. Thereupon, the compound may be compressedas the interface surfaces progress towards one another. If the compoundis allowed to remain in the joint being formed, a hydrostatic fluidpressure may be developed having the potential to hydraulically damagethe gasket and/or introduce significant stress into the mating partsreducing “in-service” joint efficiency. The gasket of this invention isprovided with a venting feature which allows for the relief of thedeveloping fluid pressure, but which, advantageously, does not interferewith the sealing function of the gasket and avoids introduction ofhydraulic stresses in the connection beyond those normally developedduring assembly.

[0009] The gasket herein involved is generally of a closed geometricshape and includes a generally planar, preferably metal, retainer andone or more seal elements supported on at least one and, typically, bothsides of the retainer. Advantageously, the retainer delimits thecompression of the seal elements to avoid an avoid-compressed condition,and also provides for a direct load path between the interface surfacesto accommodate the development of high bearing stresses with a minimumof torque loss.

[0010] The seal elements each may be molded of an elastomeric materialin an associated groove formed into a corresponding one of the sides ofthe retainer. Each of the seal elements may be formed as having a beador other configuration which is abuttingly contactible in a free statewith a corresponding one of the interfaces surfaces, and which iscompressible axially thereby into an energized state effecting afluid-tight seal between the interface surface and the facing side ofthe gasket. One or more channels are formed through side of the retainerto couple an unfilled void volume formed between each of the compressedseal elements and the corresponding interface surface into fluidcommunication with an internal or external environment for the ventingof the entrapped joint compound or other fluid from the void volume.

[0011] To facilitate the installation of the gasket between theinterface surfaces, the gasket further may be formed as having agenerally annular elastomeric locating member supportedcircumferentially about the inner or outer perimeter of the retainer.With such member being molded or otherwise attached to the outerperimeter of the retainer, the gasket may be coaxially mounted andretained within, for example, an internal gland of the coupling to beshipped therewith to the job site.

[0012] The present invention, accordingly, comprises the apparatuspossessing the construction, combination of elements, and arrangement ofparts and steps which are exemplified in the detailed disclosure tofollow. Advantages of the present invention include a sealing gasketconstruction which is adapted to vent entrapped fluid but which alsoexhibits reliable sealing properties and torque retention with a minimumof compression set. Additional advantages include a gasket constructionwhich may be adapted for use with various sealing assemblyconfigurations, and particularly which may be configured to be mountedinternally within a coupling for a threaded connection with a pipe,shaft, or tubing end such as for oil and gas well drilling applications.Further advantages include a gasket construction which is economical tomanufacture, and which may be made self-locating, retaining, andaligning to simplify and expedite installation. These and otheradvantages will be readily apparent to those skilled in the art basedupon the disclosure contained herein.

BRIEF DESCRIPTION OF THE DRAWINGS

[0013] For a fuller understanding of the nature and objects of theinvention, reference should be had to the following detailed descriptiontaken in connection with the accompanying drawings wherein:

[0014]FIG. 1 is a plan view of a representative embodiment of a gasketconstruction according to the present invention;

[0015]FIG. 2 is a magnified, fragmentary cross-sectional view of thegasket of FIG. 1 taken through line 2-2 of FIG. 1;

[0016]FIG. 3 is a magnified, fragmentary cross-sectional view of thegasket of FIG. 1 taken through line 3-3 of FIG. 1;

[0017]FIG. 4A is a fragmentary, cross-sectional assembly view showing apair of the gaskets of FIG. 1 as interposed between the mating interfacesurfaces of a pair of pipes, shafts, or other tubular members and athreadably-engageable coupling;

[0018]FIG. 4B is a fragmentary, cross-sectional view showing the gasketsof FIG. 1 as compressed within the assembly of FIG. 4A; and

[0019]FIG. 5 is a magnified view of FIG. 4B showing the compression ofone of the gaskets thereof in enhanced detail.

[0020] The drawings will be described further in connection with thefollowing Detailed Description of the Invention.

DETAILED DESCRIPTION OF THE INVENTION

[0021] Certain terminology may be employed in the description to followfor convenience rather than for any limiting purpose. For example, theterms “forward,” “rearward,” “right,” “left,” “upper,” and “lower”designate directions in the drawings to which reference is made, withthe terms “inward,” “inner,” or “inboard” and “outward,” “outer,” or“outboard” referring, respectively, to directions toward and away fromthe center of the referenced element, and the terms “radial” or“horizontal” and “axial” or “vertical” referring, respectively, todirections, axes, planes perpendicular and parallel to the centrallongitudinal axis of the referenced element. Terminology of similarimport other than the words specifically mentioned above likewise is tobe considered as being used for purposes of convenience rather than inany limiting sense.

[0022] In the figures, elements having an alphanumeric designation maybe referenced herein collectively or in the alternative, as will beapparent from context, by the numeric portion of the designation only.Further, the constituent parts of various elements in the figures may bedesignated with separate reference numerals which shall be understood torefer to that constituent part of the element and not the element as awhole. General references, along with references to spaces, surfaces,dimensions, and extents, may be designated with arrows.

[0023] For the illustrative purposes of the discourse to follow, theprecepts of the venting gasket construction of the present invention aredescribed in connection with the configuration thereof for use as a sealbetween the interface surfaces of a coupling and an end of a pipe,shaft, tubing, or other tubular member configured for a threadedengagement with the coupling. Assemblies of such type are shown, forexample, in U.S. Pat. Nos. 5,015,017 and 4,846,507. In view of thediscourse to follow, however, it will be appreciated that aspects of thepresent invention may find utility in other fluid sealing applicationsrequiring a flexible gasket of the type herein involved. Use withinthose such other applications therefore should be considered to beexpressly within the scope of the present invention.

[0024] Referring then to the figures wherein corresponding referencecharacters are used to designate corresponding elements throughout theseveral views with equivalent elements being referenced with prime orsequential alphanumeric designations, shown generally at 10 in FIG. 1 isa representative embodiment according to the present invention of anpressure-venting gasket configured for interposition between a matingpair of mutually-opposed interface surfaces. In basic construction,gasket 10 includes a generally annular and planar retainer, 12, and apair of generally annular seal elements, 14 a-b, each supported on acorresponding side of the retainer and extending along at least aportion thereof to be compressible intermediate the interface surfaces(not shown in FIG. 1) for effecting a fluid-tight seal therebetween.

[0025] With additional reference to the cross-sectional views of FIGS. 2and 3, retainer 12 extends in the radial directions defined by theorthogonal horizontal or radial axes referenced at 15 a-b in FIG. 1 ashaving an inner perimeter or margin, referenced at 16, and an outerperimeter or margin, referenced at 18. Together, the inner and outerperimeters 16 and 18 define a closed geometric shape which, in turn,encloses an opening, 19. Although the shape of retainer 12 is shown forpurposes of illustration to be generally circular, such shapealternatively may be elliptical, circular, or otherwise arcuate, orregular or irregular polygonal or otherwise rectilinear depending uponthe intended application.

[0026] With particular reference to cross-sectional views of FIGS. 2and, retainer 12 further is formed relative to a central or verticalaxis, referenced at 30 in FIGS. 2 and 3, which axis extends in an axialdirection generally normal to the radial direction referenced by axes15, as having mutually-opposing upper and lower radial surfaces, 32 a-b,respectively, and mutually-opposing inner and outer axial surfaces, 34a-b, respectively. Radial surfaces 32 each may be generally planar andextend generally perpendicular to axis 30 intermediate the inner and theouter perimeter 16 and 18 of the retainer 12, with the axial surfaces 34each extending generally parallel to axis 30 in defining thecorresponding inner and outer perimeters 16 and 18 of the retainer.Returning to the plan view of FIG. 1, the inner and outer perimeters 16and 18 of retainer 12 generally define, respectively, the inner andouter diametric extents of gasket 10 which are sized such that thegasket is receivable intermediate the interface surfaces to be sealed.

[0027] Retainer 12 itself may be fabricated from a metal, plastic, orother material which may be machined, cast, molded, or stamped. Suitablemetal materials for the construction of retainer 12 include aluminum,steel, stainless steel, copper, brass, titanium, nickel, and alloysthereof, with aluminum being preferred for many applications. The metalmay be anodized, plated, or otherwise for increased corrosionresistance. Depending upon its material of construction and the intendedapplication, retainer 12 may have an axial thickness, referenced at “t”in FIG. 2, defined between radial surfaces 32 a-b of between about{fraction (1/16)}-1 inch (0.15-2.5 cm), making the retainer generallyrigid within the joint to be assembled.

[0028] As is shown in the several views of FIGS. 1-3, retainer 12further is formed as having an axially-registered pair of mountinggrooves, 40 a-b, each of which may be machined or otherwise recessedinto a respective one of the radial surfaces 32 of retainer 12intermediate the inner and outer perimeter 16 and 18 thereof, and asextending substantially continuous along the closed geometry of theretainer. As may be seen best in FIG. 2, each of the grooves 40, whichmay be disposed generally coaxially the opening 19, are formed to definea channel which may be generally U-shaped or of other cross-section suchas V-shaped, and which includes an axial inner sidewall, 42 a-b,adjacent the inner perimeter 16, and an opposing axial outer sidewall,44 a-b, adjacent the outer perimeter 18 which is disposed a spaced-apartradial distance from the corresponding inner sidewall 42. A radialbottom wall, 46 a-b, extends intermediate a corresponding pair of theinner and outer sidewalls 42 and 44.

[0029] As also may be seen best in FIG. 2, each of the seal elements 14may be formed with a corresponding groove 40 as having a base portion,50 a-b supported on a bottom wall 46, and inner and outer lateralportions, 52 a-b and 54 a-b, respectively, supported on a correspondinginner or outer sidewall 42 or 44, and as having bead or lobe portion, 60a-b, each contactible by one of the interface surfaces for the axialsealing compression of the seal elements within the intendedapplication. In this regard, depending upon the location of suchinterface surface relative to the gasket 10, each of the bead portions60 may be spaced equidistant from the sidewalls 42 and 44 or,alternatively, oriented to one or the other side so as to define anannular gap with the outer sidewall 44 or, and as is shown at 62 a-b,with the inner sidewall 42. Bead portions 60 may be of any radial size,but typically will have a width, referenced at “w” in FIGS. 2 and 3,which, depending upon the size of the groove 40, may be between about0.030-0.125 inch (0.75-3 mm).

[0030] Within grooves 40, each of the bead portions 60 presentoppositely disposed, generally hemispherical bearing surfaces which inthe illustrated embodiment define a first and a second radial sealingsurface of the gasket 10. As may be seen in FIG. 1 for surface 60 a,such sealing surfaces extend along the generally circular geometry ofretainer 12 for coaxial registration with the margins of the interfacesurfaces which may surround, for example, a fluid flow passageway orchamber. It will be appreciated, however, that different and/orindependent geometries of seal elements 14 a-b and, similarly, beadportions 60 and their surfaces may be envisioned depending upon theconfiguration of the corresponding passageway or chamber, and/or of theinterfacing surfaces within the intended application.

[0031] For the axial compression of the seal elements 14 by theinterface surfaces effecting a fluid-tight seal therewith, the beadportions 60 thereof may be provided, again as depending upon thegeometry of the interface surfaces, to extend axially beyond thecorresponding radial surface 18 of retainer 12 for abutting contact witha corresponding one of the interface surfaces. That is, bead portions 60may be provided, as is shown in FIG. 2 to protrude between about 1-100mils (0.025-2.5 mm) beyond the corresponding radial surface 32, with thegap portions 62 being provided to accommodate the deformation of thebead portions 60 such that the surfaces thereof each may lie coplanarlywith a corresponding one of the retainer surfaces 32 when the sealelements 14 are energized between the interface surfaces. Bead portions60 may be single as shown or, alternatively, double to providedredundant scaling surfaces for each of the interface surfaces.

[0032] As aforementioned, retainer 12 may be formed as a metal stampingwith grooves 40 being stamped or machined therein. With retainer 12being provided as has been described, each of the seal elements 14 maybe adhesively bonded, interference fit or, preferably, molded, orother-wise attached to or supported on walls 42, 44, and 46 of eachgroove 40 as a preferably continuous or, alternatively, discontinuous orsegmented annulus of an elastomeric material. For the attachment of theseal elements 14 to the groove walls, the surfaces thereof may be primedwith a siloxane, silane, or other bonding agent. The primed retainer 12then may be placed into a heated molded cavity for the injection,compression, or transfer molding of an uncured rubber or otherelastomeric compound forming the integral seal elements. Each of theseal elements thereby may be formed and cured-in-place as vulcanizeddirectly onto retainer 12. Alternatively, the elastomeric elements maybe molded in a separate operation and otherwise bonded using an adhesiveor interference fit into the groove 40.

[0033] Seal elements 14 may be formed of a synthetic rubber whichspecifically may be selected for high temperature performance orotherwise for compatibility with the fluid being handled. Suitablematerials include natural rubbers such as Hevea, as well asthermoplastic, i.e., melt-processible, or thermosetting, i.e.,vulcanizable, synthetic rubbers such as fluoropolymers, chlorosulfonate,polybutadiene, polybutadiene, buna-N, butyl, neoprene, nitrile,polyisoprene, silicone, fluorosilicone, copolymer rubbers such asethylene-propylene (EPR), ethylene-propylene-diene monomer (EPDM),nitrile-butadiene (NBR) and styrene-butadiene (SBR), or blends such asethylene or propylene-EPDM, EPR, or NBR. The term “synthetic rubbers”also should be understood to encompass materials which alternatively maybe classified broadly as thermoplastic or thermosetting elastomers suchas polyurethanes, silicones, fluorosilicones, styrene-isoprene-styrene(SIS), and styrene-butadiene-styrene (SBS), as well as other polymerswhich exhibit rubber-like properties such as plasticized nylons,polyesters, ethylene vinyl acetates, and polyvinyl chlorides. As usedherein, the term “elastomeric” is ascribed its conventional meaning ofexhibiting rubber-like properties of compliancy, resiliency orcompression deflection, low compression set, flexibility, and an abilityto recover after deformation, i.e., stress relaxation.

[0034] Advantageously, seal elements 14 exhibit a reduced yield stressas compared to retainer 12 and, accordingly, are deformable forconforming to irregularities existing between the interface surfaces ofthe pipe flanges. As will be more fully appreciated hereinafter, asgiven compressive load is applied to the seal elements 14, an increasedbearing stress is provided thereon by virtue of the reduced surface areacontact of the bearing surfaces of the bead portions 60 on the interfacesurfaces. This increased stress will be sufficient to exceed the reducedyield stress of the seal elements 14 for the deformation thereofeffecting the fluid-tight sealing of the interfacing surfaces. Indeed,the seal elements may be used to effect a hermetic seal which isespecially useful in petrochemical and other applications to control thefugitive emission of VOC's and other pollutants.

[0035] In service, it will be observed that the combination of arelatively incompressible retainer 12 and the relatively compressibleseal elements 14 provides a gasket construction which minimizes torqueloss and thereby obviates much of the need for the periodic re-torquingof the members being joined. That is, it is well-known that gaskets ofthe type herein involved may develop a compression set which ismanifested by fluid leaks as the tension in the joint is relaxed and thefluid-tight sealing of the interfacing surfaces is compromised. In thisregard, the provision of bead portions 60 ensures positive sealing, withretainer 12, in turn, synergistically providing generally a compressionstop and non-yielding contact in establishing an alternative load torquepath minimizing the compression set and leak potential of the gasket 10.Thus, the use of a retainer allows the mating parts to bear stress loadswhich otherwise would cause the deformation or extrusion of a gasketwhich lacked a retainer. In the case of a metal retainer 12, suchcontact additionally affords improved heat transfer between theinterface surfaces, and also develops relatively high seal stresses forassured fluid-tight sealing of the interfacing structures.

[0036] Returning to the plan view of FIG. 1 and with additionalreference to the cross-sectional view of FIG. 3, with the reverse sideof gasket 10 hidden from view in FIG. 1 being understood to beduplicative to the side shown, it may be seen that retainer 12 isfurther formed as having at least one and, preferably, a plurality ofchannels machined, molded, stamped, or otherwise formed into each of theradial surfaces 32, such channels formed into surface 32 a beingcommonly referenced at 70 a in FIGS. 1 and 3, and with one of suchchannels formed into surface 32 b being referenced at 70 b in FIG. 3.Each of the channels 70 is formed into a corresponding radial surface 32to extend radially through a corresponding one of the inner or outersidewall 42 or 44 of each groove to define an opening, referenced at 72a-b in FIG. 3 therein, and through the adjacent one of the retainerinner or outer perimeter 16 or 18. In the embodiment shown in FIGS. 1-3,each of the channels may be seen to be formed though the inner sidewall42 and the inner perimeter 16 for the venting of fluid into the opening19 of the retainer 12. Alternatively, however, and depending upon therequirements of the particular application, channels 70 may be formed toeach extend through the outer sidewall 44 and the outer perimeter 18 forthe venting of fluid out of the retainer 12. As may be seen best in theplan view of FIG. 1 for channels 70 a, each of the channels 70 may bespaced-apart radially at about the same angular distance from eachadjacent channel 70.

[0037] Each of the channels 70 may be formed as having a pair ofopposing axial end walls, 74 a-b and 76 a-b (with walls 74 b and 76 bbeing hidden from view in FIG. 1, and with walls 76 a-b being hiddenfrom view in FIG. 3), respectively, spaced-apart angularly about axis 30to define a radial widthwise extent of the channel therebetween, anddisposed generally normal the groove inner sidewall 42. Channels 70 areeach further formed as having a radial bottom wall, 78 a-b, extendingintermediate each pair of end wall 74 and 76 such that, and as may beappreciated with reference to FIG. 3, each channel 70 has a generallyU-shaped cross-section. As also may be seen in FIG. 3, each of thechannel bottom walls 78 may be disposed axially generally intermediatethe corresponding radial surface 32 and the corresponding groove bottomwall 46 so as to define the depth, commonly referenced at “d” in FIG. 3of each channel which may be between about ⅛-¼ of the axial thickness t.

[0038] Referring now to the assembly views of FIGS. 4A and 4B, arepresentative joint assembly incorporating gasket 10 of the presentinvention is shown generally at 100. An alternative joint assembly isdescribed in U.S. application Ser. No. 09/922,410, the disclosure ofwhich is incorporated herein by reference.

[0039] Within joint assembly 100, gasket 10 of the present invention isinterposed between a pair of mutually-facing, axially spaced-apartinterfaces surfaces, 102 a-b, one of which surfaces, surface 102 a, maybe the end face of a pipe, shaft, tubing, or other tubular member, 104,and the other of which surfaces, 102 b, may be an internal shoulder,ledge, land, or the like formed within a tubular coupling, 106, which isfurther configured for a threaded engagement with the pipe end 104. InFIGS. 4A and 4B, assembly 100 is shown to be generally symmetrical aboutthe axis referenced at 107 such that a second gasket 10′, interfacesurfaces 102 a′-b′, and pipe end 104′ are provided, with the view ofgasket 10 being shown to correspond to the cross-sectional view of FIG.3, and the view of gasket 10′ being shown to correspond to thecross-sectional view of FIG. 2. Coupling 106 thus is used to connect thepipe ends 104 and 104′ together, with the gaskets 10 and 10′ beingemployed to provide a fluid-tight seal between the pipe ends 104, 104′and the coupling 106 for the conveyance of fluid through the passageway,referenced at 108, thereby defined through the joined pipes andcoupling. In this regard, gaskets 10 and 10′ each are disposed betweentheir associated interface surfaces 102 a-b and 102 a′-b′ in generalcoaxial registration with passageway 108.

[0040] Further in this regard, each of the gaskets 10 and 10′ may bereceived within an internal gland, 110 and 110′, formed within thecoupling 106. Glands 110 and 110′ have a given inner diametric extent,111 and 111′, with the outer perimeters 18 and 18′ of retainers 12 and12′ each being sized to be received coaxially therein. For the positiveretention of the gaskets 10 and 10′ within the glands, retainers 12 and12′ may be provided with a generally annular elastomeric locatingmember, 112 and 112′, respectively. Each of the glands 110 and 100′ alsomay be configured as having a snap surface feature in the mannerdescribed in U.S. application Ser. No. 9/922,410.

[0041] As may be seen with additional reference to FIG. 2, locatingmember 112, which may be formed of the same or a different elastomericmaterial as the seal elements 14, may be received circumferentiallyabout the retainer outer perimeter 18 as molded, bonded, interferencefit, or otherwise supported on outer axial surface 34 b, and as having aselect outer diametric extent, referenced at 114. Returning to FIGS. 4Aand 4B, such outer diametric extent 114 and 114′ of locating members 112and 112′ may be seen to be sized to interferingly engage the innerdiametric extent 111 and 111′ of glands 110 and 110′ effecting theretention of the gaskets 10 and 10′ therein.

[0042] With continuing reference to FIG. 4A, with gaskets 10 and 10′interposed therebetween, the interface surfaces 102 a-b and 102 a′-b′are shown to be spaced-apart along a longitudinal axis, 120, and will beunderstood to be axially displaceable therealong as the pipe ends 104and 104′ and/or the coupling 106 are tightened. With a corresponding oneof the interface surfaces 102 a-b and 102 a′-b′, each of the grooves 40a-b and 40 a′-b′ define the void volume referenced at 122 a-b for gasket10.

[0043] Turning now to FIG. 4B, and with additional reference to themagnified view of gasket 10 shown at 128 in FIG. 5, as the surfaces 102a-b and 102 a′-b′ are displaced into abutting contact with thecorresponding radial surfaces 32 a-b and 32 a′-b′, seal elements 14 a-band 14 a′-b′ each are contacted by a corresponding interface surface 102a-b or 102 a′-b′, and are compressed therebetween and a correspondinggroove bottom wall 78 a-b or 78 a′-b′ (not referenced in FIG. 4B forclarity) from the free state shown in FIG. 4A into the energized stateshown in FIG. 4B effecting a generally fluid-tight seal between each ofthe retainers 12 and 12′ and the interface surfaces 102 a-b and 102a′-b′. In FIG. 4B, it may be seen that the radial surface 32 a-b and 32a′-b′ of each of the gaskets 10 and 10′ each define a radial innerportion, referenced at 130 a′-b′ for gasket 10′ and at 130 a-b in FIGS.2 and 5 for gasket 10, and a radial outer portion, referenced at 132a′-b′ for gasket 10′ and at 132 a-b in FIGS. 2 and 5 for gasket 10,between, respectively, the retainer inner perimeter 16 and 16′ and thegroove inner sidewall 42 a-b and 42 a′-b′, and the retainer outerperimeter 18 and 18′ and the groove outer sidewall 44 a-b and 44 a′-b′.Such portions 132 and 132′ each provide a bearing surface contact withthe corresponding one of the interface surfaces 102 and 102′ and apositive stop delimiting the compression of the seal elements 14 and 14′to thereby avoid the over-compressed thereof during installation ormaintenance.

[0044] In the energized state of FIG. 4B, each of the seal elements 14a-b may be seen to occupy a filled portion of the corresponding voidvolume 122 a-b, with the remainder thereof being an empty or unfilledportion. Each of the channels 70 a-b are coupled through a correspondingopening 72 a-b in fluid communication with the unfilled portion acorresponding one of the void volumes 122. In this regard, each of thechannels 70 define with a corresponding interface surface 102 a vent forrelieving hydrostatic fluid pressure, such as from the compression ofjoint compound extruded from between the thread of the pipe ends 104 andthe coupling 106, from the unfilled portion of the void volume and intothe passageway 108 as indicated by the arrows commonly reference at 140for gasket 10.

[0045] Thus, a unique gasket construction for pipe or shaft couplingsand other commercial, industrial, or military applications is describedwhich exhibits reliable sealing properties while providing for theventing of internal fluid pressure.

[0046] As it is anticipated that certain changes may be made in thepresent invention without departing from the precepts herein involved,it is intended that all matter contained in the foregoing descriptionshall be interpreted in as illustrative rather than in a limiting sense.All references including any and all priority documents cited herein areexpressly incorporated by reference.

What is claimed is:
 1. An assembly for joining a tubular first sectionto a tubular second section, each of the sections having anexternally-threaded end terminating at an end face disposable aspaced-apart distance from an opposing surface along a longitudinalaxis, and the sections being rotatably displaceable in an axialdirection along the longitudinal axis to move each of the end facestowards its opposing surface, the assembly comprising: a generallytubular coupling comprising: a first coupling end and a second couplingend opposite the first coupling end, each of the first and secondcoupling ends being internally-threaded to be threadably engageable withan end of a corresponding one of first and second sections for therotational displacement thereof along the longitudinal axis; and a firstseating portion defined intermediate the first and second coupling ends;and at least a first gasket seatable in the seating portion between,when the first section end is threadably engaged with the coupling firstend, the end face of the first section and the surface opposing thefirst section end face, the first gasket comprising: a retainer havingopposing first and second radial surfaces, each of the first and secondradial surfaces extending in a radial direction generally normal to theaxial direction intermediate an inner perimeter and an outer perimeterwhich together define a closed geometry registrable between the firstsection end face and its opposing surface, the retainer including agenerally annular first mounting groove formed in the first radialsurface intermediate the inner and outer perimeter and extendingsubstantially continuously along the closed geometry, the first mountinggroove defining a first void volume between the first section end faceand being formed as having an axial first inner sidewall adjacent theinner perimeter and an opposing axial first outer sidewall adjacent theouter perimeter disposed a spaced-apart radial distance from the firstinner sidewall, and as having a radial first groove bottom wallextending intermediate the first inner and the first outer sidewall; anda generally annular first seal element received in the first mountinggroove to extend therein substantially continuously along the entiretyof the closed geometry, the first seal element configured in a freestate to be compressible axially intermediate the first groove bottomwall and the first section end face into an energized state effecting afluid-tight sealing therewith, the first seal element occupying in theenergized state a filled portion of the first void volume, the remainderof the first void volume being an unfilled portion, wherein the firstgasket retainer further includes one or more first channels formed intothe first radial surface to extend radially through a corresponding oneof the first inner and the first outer sidewall to define an openingtherein, and through the adjacent one of the inner and the outerperimeter, each of the first channels being coupled through acorresponding opening in fluid communication with the unfilled portionof the first void volume, and defining with the first section end face avent relieving from the unfilled portion of the first void volume afirst hydrostatic pressure developed therein from a source of fluidpressure between the first section end face and the first gasket as thefirst section end face is moved towards its opposing surface.
 2. Theassembly of claim 1 wherein each of the first and the second radialsurface of the first gasket retainer is generally planar.
 3. Theassembly of claim 1 wherein the first radial surface of the first gasketretainer has a radial first outer portion defined between the firstouter sidewall and the outer perimeter, and a radial first inner portiondefined between the first inner sidewall and the inner perimeter, thefirst outer and the first inner portion being generally coplanar andeach providing a bearing surface contactible by the first section endface delimiting the compression of the first seal element.
 4. Theassembly of claim 1 wherein each of the first channels of the firstgasket retainer is formed as having a pair of opposing axial end wallsspaced-apart angularly about the longitudinal axis and disposedgenerally normal to the corresponding one of the first inner and thefirst outer sidewall, and as having a radial channel bottom wallextending intermediate the end walls.
 5. The assembly of claim 4 whereinthe channel bottom wall is disposed axially intermediate the firstradial surface and the first groove bottom wall.
 6. The assembly ofclaim 1 wherein the first gasket retainer is formed of a metal material.7. The assembly of claim 6 wherein the metal material forming the firstgasket retainer is selected from the group consisting of aluminum,steel, stainless steel, copper, brass, titanium, nickel, and alloysthereof.
 8. The assembly of claim 1 wherein the first seal element ofthe first gasket is formed of an elastomeric material selected from thegroup consisting of natural rubbers and synthetic rubbers.
 9. Theassembly of claim 1 wherein the first seal element of the first gasketis configured as having one or more bead portions, each of the beadportions being contactible by the first section end face for thecompression of the first seal element and forming in the energized statethereof a radial sealing surface with the first section end face. 10.The assembly of claim 1 wherein the seating portion of the coupling hasgiven inner diametric extent, and wherein the first gasket furthercomprises a generally annular elastomeric locating member supportedcircumferentially about the outer perimeter of the retainer, the firstgasket being receivable coaxially within the inner diametric extent ofthe coupling seating portion, and the locating member having an outerdiametric extent sized to interferingly engage the inner diametricextent and retain the first gasket therewithin when the first gasket isreceived coaxially in the coupling.
 11. The assembly of claim 1 whereinthe first and the second radial surface of the first gasket retainerdefine a maximum axial thickness dimension of the retainer therebetween,the dimension being between about {fraction (1/16)}-1 inch (0.15-2.5cm).
 12. The assembly of claim 1 wherein the first gasket retainerfurther includes: a generally annular second mounting groove formed inthe second radial surface intermediate the inner and outer perimeter andextending substantially continuously along the closed geometry, thesecond mounting groove defining a second void volume between the surfaceopposing the first section end face and being formed as having an axialsecond inner sidewall adjacent the inner perimeter and an opposing axialsecond outer sidewall adjacent the outer perimeter disposed aspaced-apart radial distance from the second inner sidewall, and ashaving a radial second groove bottom wall extending intermediate thesecond inner and the second outer sidewall, the first gasket furthercomprising a generally annular second seal element received in thesecond mounting groove to extend therein substantially continuouslyalong the entirety of the closed geometry, the second seal elementconfigured in a free state to be compressible axially intermediate thesecond groove bottom wall and the opposing surface into an energizedstate effecting a fluid-tight sealing therewith, the second seal elementoccupying in the energized state a filled portion of the second voidvolume, the remainder of the second void volume being an unfilledportion; and one or more second channels formed into the second radialsurface to extend radially through a corresponding one of the secondinner and the second outer sidewall to define an opening therein, andthrough the adjacent one of the inner and the outer perimeter, each ofthe second channels being coupled through a corresponding opening influid communication with the unfilled portion of the second void volume,and defining with the opposing surface a vent relieving from theunfilled portion of the second void volume a second hydrostatic pressuredeveloped therein from a source of fluid pressure between the opposingsurface and the first gasket as the first section end face is moved inthe axial direction towards the opposing surface.
 13. The assembly ofclaim 12 wherein the second mounting groove is aligned in axialregistration with the first mounting groove.
 14. The assembly of claim 1wherein the end faces of the first and second sections aremutually-opposing, the second section end face defining the opposingsurface of the first section end face, and the first section end facedefining the opposing surface of the second section end face.
 15. Theassembly of claim 1 wherein: the seating portion is configured as havingmutually-opposing first and second shoulders which define, respectively,a first seating surface disposed opposite the first section end face andwhich defines the opposing surface thereof, and a second seating surfacedisposed opposite the second section end face when the second sectionend is threadably engaged with the coupling second end and which definesthe opposing surface of the second section end face, the first gasketbeing seatable in the seating portion on the first seating surface; andthe assembly further comprises a second gasket seatable in the seatingportion on the second seating surface between, when the second sectionend is threadably engaged with the coupling second end, the end face ofthe second section and the second seating surface, the second gasketcomprising: a retainer having opposing first and second radial surfaces,each of the first and second radial surfaces extending in a radialdirection generally normal to the axial direction intermediate an innerperimeter and an outer perimeter which together define a closed geometryregistrable between the second section end face and the second seatingsurface, the retainer including a generally annular first mountinggroove formed in the first radial surface intermediate the inner andouter perimeter and extending substantially continuously along theclosed geometry, the first mounting groove defining a first void volumebetween the second section end face and being formed as having an axialfirst inner sidewall adjacent the inner perimeter and an opposing axialfirst outer sidewall adjacent the outer perimeter disposed aspaced-apart radial distance from the first inner sidewall, and ashaving a radial first groove bottom wall extending intermediate thefirst inner and the first outer sidewall; and a generally annular firstseal element received in the first mounting groove to extend thereinsubstantially continuously along the entirety of the closed geometry,the first seal element configured in a free state to be compressibleaxially intermediate the first groove bottom wall and the second sectionend face into an energized state effecting a fluid-tight sealingtherewith, the first seal element occupying in the energized state afilled portion of the first void volume, the remainder of the first voidvolume being an unfilled portion, wherein the second gasket retainerfurther includes one or more first channels formed into the first radialsurface to extend radially through a corresponding one of the firstinner and the first outer sidewall to define an opening therein, andthrough the adjacent one of the inner and the outer perimeter, each ofthe first channels being coupled through a corresponding opening influid communication with the unfilled portion of the first void volume,and defining with the second section end face a vent relieving from theunfilled portion of the first void volume a first hydrostatic pressuredeveloped therein from a source of fluid pressure between the secondsection end face and the second gasket as the second section end face ismoved towards the second seating surface.
 16. The assembly of claim 15wherein the seating portion is further configured as having a radiallyinwardly-extending first snap surface disposed adjacent the firstseating surface an axially spaced-apart distance therefrom, and aradially inwardly-extending second snap surface disposed adjacent thesecond seating surface an axially space-apart distance therefrom, thefirst snap surface being configured to interferingly retain the firstgasket on the first seating surface, and the second snap surface beingconfigured to interferingly retain the second gasket on the secondseating surface.